Variable speed apparatus



June 9, 1942. s. GROSSENBACHER- ARIABLE SPEED APPARATUS y Filed Ju ly 19. 1939 5 Sheets-Sheet 1 Jdne 9, 1942.

E. GROSYSENBACHER VARIABLE ,SPEED APPARATUS 5 Sheets-Sheet 2 Filed July 19, 1939 INVENTOR g lien 57 630$$-64 45 Y Y C j g ATTORNEY 5 Sheets-Sheet 5 ma 0% m A. v m \Y\ 6 H a g mm m E m A m MM 0 .o a R b a v Q r N R s a %v 5 WV \xm O Q, N .R-,\ N R m m E. GROSSENBACHER VARIABLE SPEED APPARATUS Filed July 19, 1959 June 9, I942.

June 9, 1942- E. GROSSEN BACHERIJ 2, ,4

VARIAB E SPEED APPARATUS Filed July 19, 19:59 5 Sheets-Sheet 5 QWNY o o Patented June 9, 1942 V UNITED STATES TENT OFFICE VARIABLE SPEED APPARATUS Ernest Grossenbacher, Fajardo, P. R.

Application July 19, 1939, Serial No. 285,296

3 Claims.

The invention relates to variable speed apparatus and hasfor its object to provide an improved apparatus for transmitting operating power from a prime mover to an operated mechanism or machine. The invention contemplates further the provision of a variable speed apparatus whereby the output speed, for instance of an output shaft may be accurately maintained at any .point between zero and maximum in a simple and reliable manner. Other more specific objects will appear from the description hereinafter and the features of novelty will be pointed out in the claims.

In the accompanying drawings, which illustrate examples of the invention without defining its limits, Fig. l is a plan view of the apparatus; Fig 2 is a side elevation thereof Fig. 3 is a detail section of a governor controlled valve included in the apparatus; Fig. 4 is a fragmentary plan View of a manually operated control; Fig. 5 is a detail end View looking from the left in Fig. 2; Fig. 6 is an enlarged detail section on the line 6-6 of Fig. 5; Fig. 7 is a detail section on the line l'! of Fig. 1; Fig. 8 is a sectional plan view of another form of the apparatus; Fig. 9 is a fragmentary plan view of the form shown in Fig. 8; Fig. 10 is a section on the line Ill- H1 of Fig. 8, and Figs. 11, 12, and 13 are views illustrating three additional forms of the apparatus respectively. i

The apparatus shown in Figs. 1, 2, and 3 comprises a rotative speed starting and regulating device employing a planetary drive and hydraulic speed control consisting of a revolving multiple cylinder pump and speed governor.

The planetarydrive comprises a gear housing l5 formed with an external. annular gear l6 and aninternal annular gear H with a tubular hub I8 projecting from the housing [5 in registry.

with the axis thereof as shown in Fig. l. A cover plate I9 is removably secured to the housing [5 in any convenient manner as by screws 28, and includes a tubular bearing hub 2i projecting from said cover plate IS in registry with the axis of the housing !5 as illustrated in Fig. l. The housing 15 and its associated elements are rotatably mounted by means of the hubs l8 and 2! in bearing 22 and 23 carriedby upright pedestals 24 which project upwardly from the base 25. The

latter, in the illustrated example, is constructed in the form of a tray or receptacle for reasons to be set forth more fully hereinafter.

A speed regulating shaft 26 is journalled in and extends axially through the bearing hub 21 and at its outer end externally of the hub 2| carries a pinion 21, said shaft at its inner end,

- interiorly of the housing I5 being provided with a sun pinion 23. The latter meshes with planet gears 29 which in turn mesh with the internal annular gear [1 and are rotatably mounted on studs 30 fixed upon and projecting from one face of a planet disc 3| located within the housing l5 as shown in Fig. 1. The planet disc 3| forms an integral part of or is fixed upon a low speed shaft 32 which is journalled in and projects outwardly beyond the tubular hub l8, The shaft 32 is further rotatably supported in and extends beyond a bearing 33 carried by an upright pedestal 34 projecting upwardly from the base 25, the projecting end'of the shaft 32 being equippedwith a keyway 35 or its equivalent for operative connection with associated mechanism or machines. The low speed shaft 32 is held against material axial displacement by a collar 36 fastened in place by a set-screw 31 in juxtaposition to the bearing 22, and a sprocket 38 carried by said shaft 32 in contiguous relation to thebearing 33.

The sprocket 38 is connected by means of a sprocket chain 39 with a sprocket pinion 40 fixed upon a shaft 4| journalled in a bearing 42 supported by a bracket 43 upon an upright frame 44. The latter is superimposed upon a valve casing 45 which in turn is fixed upon a bracket 46 comprising part of or secured to the bearing 22. The shaft 4| further is provided with a bevel pinion 41 in mesh with a co-operating bevel pinion 43 rotatably mounted on the frame 44 and carrying a speed governor 43 as illustrated in Fig. 2. The governor 49 is of the form of a conventional steam engine governor but with inverted valve motion. In other words, instead of closing the" governor controlled valve as the speed increases, the illustrated governor 49 opens said valve. I

As shown in Fig. 3, the valve casing 45 is formed with an internal chamber 59 having a port 5! and provided with a stationary tubular sleeve 52 fixed in place in any convenient mani ner and having ports 53 communicating with the chamber 58. A cylindrical tubular valve 54 open at its one end to the interior of the casing 45 is slidably fitted in the sleeve 52 and includes ports 55 co-operating with the previously mentioned ports 53 to control communication begovernor re and is slidably mounted in a suitable portion of the frame 44 as illustrated in Fig. 3. With this arrangement, the valve :3 is slidably operated in the sleeve 52 by the fiyball action of the governor 39. In other words, while the governor 45 is at rest, the valve 54 occupies the raised position shown in Fig. 3 in which the ports 55 are out of registry with the ports 53 and communication between the casing ports 55 and 53 is consequently cut off. When the governor 65 revolves, the movable head 58 thereof will be moved downwardly by the fiyball action of said governor and will correspondingly operate the governor rod 5? to thereby shift the valve 54 downwardly in the sleeve 52. As a result of this, the ports 55 will be adjusted into partial or complete registry with the ports 53 to thereby establish partially open or fully open communication between the casing ports 5| and 56. Variations in the extent to which the ports 55 are adjusted into registry with the ports 53 is dependent upon the speed at which the governor 49 rotates.

The apparatus being described further includes an auxiliary reversible rotary pump 59 mounted upon a bracket 6% fastened to the bearing 23 as shown in Fig. l. The pump 59 is operated by means of a gear 5i fixed upon the pump shaft and meshing with an annular gear 62 carried by and constituting an integral part of the cover plate I 9 attached to the housing I 5.

In addition to the parts so far mentioned, the apparatus of Figs. 1 and 2 embodies a rotating cylinder variable displacement pump 63 mounted upon the base 25 and consisting of a cylindrical casing 64 which includes a tubular hub 55 projecting therefrom in registry with the axis of said casing 66 as illustrated in Fig. 1. On its interior circumferential surface the casing 64 is formed with internal grooves (-56 and 61, the opposed ends of which are separated from each other by diametrically opposite partitions 63 as shown in Fig. '7. A cylindrical body 69 is rotatively mounted in the casing 63 with its circumferential surface in snug contact with the inner circumferential surface of the casing 64.

The cylindrical body 59 is carried by and preferably forms an integral part of a shaft III journalled in and projecting outwardly beyond the tubular hub 65. The shaft I9 has fixed thereon the gears II and I2, the latter of which meshes with the pinion 21 on the shaft 26.

As illustrated in Fig. '7, the cylindrical body 69 of the variable displacement pump 63 is provided with four radially disposed cylinders I3 for the slidable accommodation of pistons Id. The latter are connected by means of connecting rods I5 with a movable pin it comprising part of means whereby the strokes of the pistons I4 are varied as will appear more fully hereinafter.

The cylindrical body 55 is formed with an axial bore into which the pin I5 projects from a block 'II slidable in a transverse slot I8 provided in a cover plate I?! which closes the front of the casing 64 and is remcvably fastened in place by screws 85. The block I? is carried by and preferably comprises part of a stroke adjusting slide BI adjustably mounted in a slotted boss or guide 82 projecting from the outer face of the cover plate 15. A plate 83 fastened to the boss or guide 82 by screws 84 maintains the slide Si in place therein without interference with the adjustability of said slide 8I in said boss or guide 82, as shown in Fig. 1.

The stroke adjusting slide 6| is provided with a transverse rectangular slot 85 for slidably accommodating a shift member 85 mounted by means of a pin 81 upon the circular head 88 of a control shaft 89, said head 83 being rotatably fitted into the upper portion of the boss or guide 82 and contiguous portion of the plate 83 as illustrated in Figs. 5 and 6. The shaft 89 is further rotatably supported in a bearing 95 carried by a bracket 9| suitably mounted on the boss or guide 82, and at its upper end carries a cam 92 fixed on said shaft 89 by means of a key 93 and nut 95, A cam gear 95 is loosely mounted upon the shaft 35 in engagement with the bearing 95, so that said cam gear 95 is capable of rotating relatively to said shaft 65 and cam 92. A lug or projection 95 is carried by the cam gear 95 and extends from one face thereof for engagement with the cam 92 as will be more clearly set forth hereinafter. On its periphery the cam gear 95 is formed with a depressed cam 9'I, and further is provided throughout a portion of said periphery with worm gear teeth 98. The latter are in mesh with a worm screw 99 fixed upon a regulating shaft I60 rotatably supported in a bearing bracket or frame Iiil which is pivotally connected by means of a bolt I I32 with an extension of the bracket 9|. An operating hand wheel I93 is mounted upon the outer ends of the shaft I and is fixed in place thereon by means of a nut I04. A diaphragm casing I35 is provided with an internal diaphragm I28 connected with a stem III! which in turn is connected with the bearing frame II]! at IE8 and carries a spring I59 bearing with one end against the casing I95 and with its other end against the diaphragm I58 as shown in Fig. 4. The diaphragm casing I85 is fixed in place by a bracket III} suitably attached to the bracket BI as illustrated in Fig. 5. A pipe III communicates with the diaphragm casing IEI5 and supplies the same with oil or its equivalent under pressure whereby the diaphragm Ill-5 is operated against the tension of the spring I59 to normally maintain the worm screw 99 in mesh with the worm teeth 98 of the cam gear 95.

A roller II 2 is normally located in the de- I pressed cam 91 of the cam gear and is rotatably mounted on one arm of a bell-crank lever I !3 pivoted on a stud I I4 fastened to the bracket 9|. The other arm of the bell-crank lever H3 engages a clutch push rod H5 slidably mounted in stationary bearings I I6 and coupled, by means of a connecting rod I H, to an auxiliary push rod H8 which is slidably supported in stationary bearings H9 and carries the clutch shifter I20. A spring I2! is located on the auxiliary push rod H8 between the connecting rod II? and one of the bearings H9 as illustrated in Fig. 4 and serves normally to maintain the clutch I22 in its operative position. The clutch I22 is slidably mounted on the input or high speed shaft I23 and is held to rotate therewith by means of a key I24 or its equivalent. The clutch I22 serves, in its operative position to cause a pinion I25 which meshes with the gear H on the shaft IQ of the cylindrical body 69, to rotate with the input or high speed shaft I23, and in its inoperative position, to enable said shaft I 23 to rotate independently of and relatively to said pinion I25, the latter being held against axial movement on the shaft I23 by the clutch I 22 and a collar I26. The shaft I23 is journalled in bearings I21 supported by pedestals I28 mounted on the base 25 and is fixed against longitudinal displacement in said bearings I2'I by collars I 29 as shown in Fig. 1. A spur pinion I 30 is fastened on the high speed shaft I23 to rotate therewith, and meshes with the external annular gear I6 of the housing I as illustrated in Figs. 1 and 2.

The suction side of the auxiliary pump 59 is in communcation with a pipe I3l provided at its lower end with a foot valve I32 located in the tray or receptacle constituting the base of the apparatus, and submerged in the oil I33 or its equivalent located in said tray or receptacle 25 as shown in Fig. 2. A pipe I34 leads from the discharge side of said auxiliary pump 59 and terminates in a relief valve I35, the discharge port of which is connected by means of a pipe I36 with an oil tank (not shown) which serves the lubricating system of the apparatus. Branch connections I3! and I38 provided respectively with check valves I39 and I40 lead from the pipe I34 to upper and lower oil circulating pipes MI and I42 respectively, the latter being connected with each other at one end by a pipe I43 and having their other ends in communication with a double check valve I44 which in turn is connected by means of a branch pipe I45 with a safety valve I46. A branch connection I4I leads from the upper pipe I M to an upper port I40 of the variable displacement pump 63 and a similar branch connection I49 leads from the lower pipe I42 to a lower port I50 of said variable displacement pump 63. The ports I48 and I50 are in communication respectively with the internal grooves 66 and 61 of the pump casing 64.as shown in Fig. '7.

A three-way stop cock I5I and a straight-way cock I52 are located in spaced relation to each other in the upper oil circulating pipe I4I, the latter being connected at a point between the cocks I5I and I52 with the port 5I of the governor valve casing 45 by means of a branch pipe 553 as illustrated in Fig. 1. The port 56 of the governor valve casing 45 in turn is connected by means of a pipe I54 with the lower oil circulating pipe I42.

In practice a prime mover such as an electric motor, is operatively connected in any convenient manner with the input or high'speed shaft I23. When said prime mover is in operation the shaft I23 is actuated and rotative power is transmitted through the clutch I22, which is in its operative position, to the pinion I25 which in turn operates the large gear. II and the smaller gear I2, both mounted on the shaft I0 of the variable displacement pump 63, to thereby operate said pump shaft I0. At the same time the smaller gear I2 will rotate the pinion 21 and its shaft 26 and correspondingly operate the suns pinion 28. The rotation of the input or high speed shaft I23 will also rotatively actuate the pinion I30 which accordingly transmits rotative motion to the external annular gear I6. brings about a rotation of the housing I5 and with it the internal annular gear II.

Since the gear ratio of gear train of gears I25-II?2-2I-28, is equal to the gear ratio of gear !39-I6II but in the opposite direction, the planetary gears 29 receive from both gear trains the same rotative speed and therefore simply revolve in a stationary position around the axes 30.

Although at this stage all gears revolve, the planetary gears 29 do not move in planet circle around sun pinion 28. Since this isthe case, the axes 39 of the planetary-gears 29 mounted to planet disc 3I and consequently the output shaft 32 remain'in a locked position. By manually revolving the speedregulating whe'el I03 This and its shaft I and worm screw 99 which meshes with the worm teeth 98, to thereby turn the cam gear 95, the roller II2 passes out of the depressed cam 91. The bell-crank lever H3 is thereby pivotally actuated on the stud II 4 and pushes the pushrod H5 and auxiliary pushrod II8 forward, to correspondingly shift the clutch shifter I20 in a manner to disengage the gear I25 from the clutch I22. At this stage, the lug or projection 96 on the cam gear engages the cam 92 which is keyed to the shaft 89.

Since the pin I6 of the block 11 and stroke adjusting slide BI up to this point has been concentrically located relatively to the cylindrical body 69 which at this stage is revolving in the casing 64 of the variable displacement pump 63, the connecting rods I5 have exerted no pumping action on the pistons I4. As the manual operation of the speed regulating wheel I03 is continued, the lug 96, by acting on the cam 92 will rotate the shaft 89 and thereby will cause the block 86 in co-operation with the slot 85 to shift the stroke adjusting slide 8| in the boss 82. The pin I6 will thereby be moved in a direction dependent upon the direction of operation of the wheel I93 away from its concentric position. When the pin I6 is thus shifted from its concentric position, and the cylindrical body 69 continues to revolve the pistons I4start their pumping action and the displacement in the cylinders I3 increases with increase of the eccentricity of pin I6 relative to cylindrical body 69.

As the housing I5 is rotated by the pinion I30 acting on the external annular gear I6, the gear 62 will be correspondingly actuated and in turn will transmit movement to the gear 6| and thereby operate the auxiliary pump 59. Thelatter draws oil I33 or its equivalent from the base 25 upwardly through the pipe I3I and discharges said oil or its equivalent through the pipe I34 from which its passes through the pipes I31 "and I38 and the check valves I39 and I40 to the upper and lower oil circulating pipes MI and I42 respectively.

The three-way stop cock I5I in the upper pipe I4I serves to direct the oil either to the governor valve casing 45 or to permit it to circulate through straightway stop cock I52 down through pipe I43 to lower oil circulating pipe I42. At

the branch connection I41 leading from the upper oil circulating pipe I II, the oil passes to and from (depending on direction of circulation) the upper half of variable displacement pump 64 and at the branch connection I49 from the lower pipe I42 to and from the lower half of pump 64. If the three-way cock I5! is so set that its passage is open to the governor valve casing 45, the oil passes through pipe I53. Both the upper and'low'er oil circulating pipes MI and I42 are protected against excessive pressure by the safety valve I46. The double check valve I44 is designed to permit passage of the oil to the safety valve I46, by opening on the high pressure side and closing toward the low pressure side of the oil circulating system.

With all gears and associated movable parts in motion with the exception of the output shaft 32 and the thereto connected chain driven governor 46, the auxiliary pump 59 will pump the oil with sufficient pressure regulated by relief valve I35, throughout the circulating system and into the variable displacement pump 64 against thepressure created by the centrifugal force of the revolving cylindrical body 69 andexpel the air along the cylinder'and piston Walls ofsaid pump. The check valves I39 and I49 prevent high pressure oil from passing from the high pressure side to the low pressure side, it being understood since the apparatus is reversible, that either circulating pipe MI and I42 may be under high pressure or low pressure. By further manipulation of the speed regulation wheel I03 and its associated mechanism, the variable displacement pump 64 forces oil against closed governor valve 54 whereby resistance is set up which retards the pumping speed. This resistance to rotation is transmitted by gear 12 to the pinion 21, the sun pinion shaft 26 and to the sun pinion 28. Since this resistance and consequent retardation upsets the speed equilibrium between sun gear 28 and internal annular gear H, the planet gears 29 compensate this speed difference by rolling around sun pinion 28 in the retarded direction thereof. As planet gears 29 are rotatably mounted on the axes 39, which are fixed parts of the disc 3I which in turn is an integral part of or connected with the output or slow speed shaft 32, this shaft starts to rotate. The slower the sun pinion 28 revolves due to pump resistance, the faster the planet gears 29 travel around said sun pinion 28 and thereby increase the rotative speed of output shaft 32. As the sprocket 38 is fixed on the output shaft 32, the rotative motion of the latter is transmitted to the governor 49 by means of the endless chain 39 and sprocket 49.

The governor 49, built on the customary flyball governor principle, in operation pushes governor rod and the thereto connected sleeve valve 54, downwardly so that the ports 55 in said 1 sleeve valve 54 register more or less with ports 53 invalve sleeve 52. This allows oil to circulate from one side of pump 64 to the other, the resistance caused by the pumping action to rotation of revolving cylindrical body 69 being increased or decreased with the variation of the load or resistance to rotative motion of output shaft 32 and thereby effecting variation of speed which are responded to by the action of the flyball governor 49. If the output shaft 32 increases its speed, the governor 49 will increase the port openings and thereby reduce the resistance of pump 64 and allow the revolving cylindrical body 69 to rotate faster, thus increasing the speed of the sun pinion 28, which decreases the speed at which the planet gears 29 travel around it. Speed adjustments may be made by manipulating the knurled headed speed adjusting screw I55 which raises and lowers the valve stem 51 and sleeve valve 54 and brings the ports 55 and 53 more or less into correlation.

Since the action of the governor 49 depends entirely upon the speed of the output shaft 32, variations in the speed of the input shaft or high speed shaft I23 do not effect the speed of said output shaft 32. The action of governor 49 affects the resistance of revolving variable displacement pump I54 allowing it to increase its speed or decrease it in accordance with the force exerted upon the sun pinion 28 and its associated gears acting on the pump and the pumping resistance caused by the governor. In other words, when the governor speed increases due to increase of speed of the input shaft I41, the governor valve 54 will open and pass more oil through the revolving cylinder pump 64, thereby reducing the pump resistance and increasing the pump speed which in turn causes the sun pinion 28 to revolve faster. An increase in speed of the sun pinion 23 decreases the planetary speed of the planet gears 29 and thereby reduces the speed of the output shaft 32 to normal or to the speed to which the governor 49 has been adjusted. The same holds for a decrease in input speed only that the cycle of action is reversed. If it is desired to effect speed variations similar to those possible with the throttle of a steam engine or controller of an electric motor, the threeway stop cock I5I is set so that circulating oil passes directly through the straight-away stop cock I52 and through connecting pipe I43 from the pipe I lI to the pipe I42, or vice-versa. With the stop cock I5I in this position, the speed governor 49 becomes ineffective. Stop cock I52 is then partly closed so that the oil passage is restricted between the pipes MI and I52. This restriction offers resistance to revolving cylinder displacement pump 64, which increases with increase of the pump stroke caused by'turning of speed regulating wheel I 93 and adjusting the therewith connected stroke adjusting slide 8I. Any speed between zero and full output speed of shaft 32 may be obtained by properly manipulating the speed regulating wheel I93, as with this device a very heavy starting torque is possible due to infinitely small starting speeds which can be maintained, it being understood that the safety valve M6 has to be set to release at a predetermined pressure to prevent excessive high pressure when starting. At the same time this safety valve I46 acts as a protective device against over-loading of the prime mover.

In the form of the apparatus shown in Figs. 8, 9, and 10, the speed control is effected by a combination of a revolving cylinder constant displacement variable speed pump with a constant speed variable displacement pump of the type hereinbefore described in connection with Figs. 1 to '7 inclusive.

As illustrated in Fig. 10, the constant speed variable displacement pump 53 is of the same general construction as the pump 59 of the form first described, and has its upper port I 48 and its lower port I59 connected by means of oil circulating pipes I41 and hi9 respectively, with the upper port I55 and lower port I51 of the variable speed constant displacement pump I58. The ports I56 and I5! lead respectively to internal grooves I59 and I59 provided on the interior circumferential surface of the casing of the pump I58 and having their opposed ends separated by diametrically opposite partitions ISI. A relief pipe I52 extends between and connects the pipes 147 and I 29 with each other, and itself is connected with opposite sides of a double check valve Ma from which a branch pipe I 15 lead to a safety valve I45? Pipes I3! and I39 provided respectively with check valves I 3.) and Hi0 connect the respective pipes I4! and I with a pipe I34 which leads to the discharge side of an auxiliary pump 59 and is provided at its upper end with a relief valve I35 the discharge port of which is connected by means of a pipe I 36 with an oil tank (not shown) which, as in the first form, serves the lubricating system of the apparatus. A pipe I3I communicates with the suction side of the auxiliary pump 59 and is provided at its lower end with a foot valve I32 located, as in the first form, in the oil contained in the tray or receptacle 25 which constitutes the base of the apparatus. The pipes I31 and I 38 through the medium of a pipe III also communicate with a diaphragm casing I95 provided interiorly with a spring and diaphragm similar to that of the casing I95; a stem IG'I connects the diaphragm of the casing It"? at I88 with the bearing frame I8I as in the form first described.

As shown in Figs. 8 and 9, the constant speed variable displacement pump 63 has mounted on its shaft 18 the gear H which meshes with a pinion I63 fixed on the high speed or input shaft I23. The constant displacement pump I58 has mounted on its shaft I64 the gear I65 meshing with the clutch pinion I25 and also carries the gear I66 meshing with the external pinion 21 of the speed regulating shaft 26. Constant displacement pump I58 has a fixed pin 18 supported by the cover 19 the latter being fastened in place by screws 88 to the casing of the pump I58. Both pumps I58 and 63 are identical in construction with each other and with the pump 63 of the first form, with the exception that the stroke or piston travel of the pump I58 is fixed i. e., the pin 18 is fixed eccentrically relatively to the revolving cylinder body 69 so that with every turn of the latter the same amount of oil is transferred and displaced from one half of the pump body to the other. The high speed or input shaft I23 to which the pinion I63 is rigidly keyed, transmits motion to the variable displacement pump I53 through the gear 1I. Clutch pinion I25 when operatively connected with the clutch I22 transmits motion through the gear I65 to the constant displacement pump I53. The pumps I58 and 63 are so arranged that the pin 16* of the constant displacement pump I58 and the pin 16 of the stroke adjusting slide 8 I, of variable displacement pump 63 have the same eccentricity relatively to the revolving cylindrical bodies 69 and revolve at the same speed. Also their rotation is such that the same amount of oil is displaced by each pump so that whatever amount of oil leaves pump I58 and flows through the pipe I41 is received by pump 63 and also that all the oil that leaves pump 63 will be received by the pump I58 through the pipe I48 Therefore, a completely closed oil circulating system exists between the two pumps I 58 and 63 Auxiliary pump 59 supplies oil to this system which is under sufficient pressure to fill pumps I58 and 63 and also compresses the spring of the diaphragm on the diaphragm casing I85 To the shaft 89 of the stroke adjusting means is fastened a rod I61 to which is attached one end of a spring I98 which is fastened at its other end to a stationary stud I69, said spring I68 serving at the proper time, to pull stroke adjusting slide 8| into full stroke position.

The planetary drive and associatedelements with which the speed varying device under discussion is connected, are-the same as described in connection with the first form of the novel arrangement.

In operation the high speed or input shaft I23 in the apparatus shown in Figs. 8, 9, and 10, receives rotative speed from the prime mover which in this case is of constant speed and transmits this speed through the pinion I63 to the gear 1I mounted on the shaft 18 of the variable displacement pump 63 The clutch pinion I25 transmits its speed to the gear I65 mounted on the shaft I64 of the constant displacement pump I58. The pumps 63 and I58 both operate at the same speed. The pinion I38 transmits its rotative speed to the external annular gear I6 and over the gear 62 to the auxiliary pump 59 which draws oil from thebase 25 and discharges it through the priming pipes I34", I31 and I38 into the revolving pumps. The pressure of the oil acts on the diaphragm I96 and compresses the travel of variable displacement pump 63 spring I89 and at the same time pushes the stem I81 outward. The stem I81 is connected to the worm bearing I8I which pivots on the bolt I82 and thereby engages worm screw 99 with the worm gear teeth 98 of cam gear 95.

Since the pumps I58 and 63 have the same ratio, due to even speed and even displacement, there exists very little resistance in driving them and as the clutch I22 is connected with the pinion I25, the gears I65 and I66 andthe pinion 21 on the speed regulating shaft 26 are all rotated so that all members revolve, except the output shaft 32, which for reasons previously explained, remains'stationary as long as the clutch I22 is in its operative position.

By turning the speedregulating wheel I83 the clutch gear I25 becomes disengaged from clutch I22 which is rigidly mounted on the high speed shaft I23. By further turning of speed regulating wheel I83 in the previously described manner, stroke adjusting slide BI with the pin 16 set fully eccentric to revolving cylindrical body 69 is shifted towards the center of said body 69, thereby reducing the strokes of the pistons 14 and with it the displacement. The'reduced displacement causes an increased pressure in the'suction line of the variable displacement pump 83 and also in the discharge side of the constant displacement pump I58. The speed of the constant displacement pump I58 is reduced in proportion with the amount of oil the variable displacement pump passes due to its reduced piston displacement at full speed. This displacement can be reduced to zero although the pump revolves at full speed, whereby the constant displacement pump I53 is brought to a full stop. It is, therefore, evident that the speed of constant displacement pump I58 depends entirely upon the piston This variation of speed of the revolving cylindrical body 69 caused by variation of oil flow to and. from the pump I58 effects the rotative speed of the gear I66 mounted on the pump shaft I64 of the constant displacement pump I58 and meshing with the gear 21 of the speed regulating shaft 26 and sun pinion 28, which by variation'of rotative speed varies the circular speed of the planet gears 29 and the thereto connected output shaft 32, as previously described with respect to the first form of the apparatus.

If the prime mover is stopped while the speed regulator is set at same fixed speed, the apparatus will automatically rest itself so that when the prime mover is brought up to full speed, the output shaft 32 can not revolve until brought up to the desired speed by manual adjustment of the speed regulating wheel I83. As soon as the machine is brought to a stop, the oil pressure effecting the diaphragm I86 ceases with the pumping action of auxiliary pump 59 The diaphragm spring I89 then pushes the diaphragm I86 in opposition to the oil and pulls with it diaphragm stem I81 connected to the worm bearing I8I and thereby disengages the worm 99 from the wormgearteeth 93. In order to reduce the piston displacement of pump 63 the shaft 89 is rotated and with it the rod I61 to which the spring I68 is attached under tension against spring stud I69. When the worm screw 99 is disengaged from worm gear teeth 98 of the cam gear 95, the spring I88 pulling on the rod I61 turns the shaft 89 and with thi motion returns stroke adjusting slide BI and the pin 16 around which the connecting rod 15 revolve to full stroke position, thereby returning pump 63 to full displacement. In this'position ball bearing roller II2 rolls into the low position of cam 91, and at the same time the bell-crank lever II 3, the clutch pushrod I15 and clutch shifter I23 are forced backward by the spring I 21 thereby engaging the pinion I2I with the clutch I22.

In the form of the apparatus first described herein, a variable displacement pump discharges against a governor or through a partly closed stop cock and starts its pumping action from zero or no displacement to full displacement, whereas in the second form the constant displacement pump and the variable displacement pump start to work with full displacement. In

the first case, operation of the output shaft begins with increased pumping action while in the second case, it increases with reduced pumping action.

In Figs. 11, 12, and 13, I have shown three different types of novel gear drives which may be utilized. As illustrated in Fig. 11 the gear drive consists of a hollow casing Ib provided with an external annular gear le and including tubular hubs I8 and 2I which project in opposite directions from said casing If: registry with the axis thereof. The hubs I3 and ZI are rotatably supported respectively in bearings 22 and 23 mounted on the base 25* in any convenient manner. Intermediate gears 29 are carried interiorly of the casing I5 on shafts 33 suitably mounted in said casing, said shafts 39 further carrying intermediate pinions 29 The intermediate gears 29 mesh with a pinion 28 fixed upon a shaft 26 which is rotatable in the bearing hub 2| a and projects outwardly beyond the same, and the intermediate pinions 29 mesh with a pinion gear I61 secured upon the output shaft 32 rotatable in the bearing hub Ic and extending outwardly beyond the same. At its outer end the output shaft 32 is provided with a keyway 35* or equivalent coupling means. The external annular gear I8 of the casing I5 meshes with a pinion 13f carried by a shaft 123 rotatable in a bearing I21 suitably supported on the base 25*.

Either of the shafts 26 or I23 may be used as the input shaft or speed regulating shaft respectively; for descriptive purposes it will be assumed the shaft I23 is the power input shaft, and that the shaft 26 is the speed regulating shaft. Under such conditions an electric motor IE8 is coupled to the shaft I23 and a convertible motor-generator IE9 is connected with the shaft 26 In operation, both the motor IE8 and the motor-generator H353 are started simultaneously and operated at speeds correlated with the gear ratios to provide an operating balance. When this balance exists, the pinion I39 m'eshing with the external annular gear It revolves the hollow casing I5 which carries with it the pinions 29 around the gear I81. As the pinions 29 and gears 2. 3 are mounted in pairs upon the shafts 30*, the gears 29 will impart rotative motion to the pinion 28 Since the speed of the motorgenerator IN is assumed to be correlated with the gear ratios, all revolving members of the apparatus are in motion, except the gear I61 and the output shaft 32*. However, as the speed of the motor-generator I69 is reduced by means of dynamic braking, the rotative speed of the gears 29 and the pinions 29 is reduced, and since the rotative speed of the casing Ifi is maintained the gear I61 and shaft 32 are rotated. With the motor I58 operating at constant speed the rotative speed of the output shaft 32 increases with a decrease in the speed of the motor-generator I69 and decreases with an increase in the speed of the latter.

The novel gear arrangement shown in Fig. 12 may also be employed in effecting variable rotative speeds. In this type of drive, the hollow casing I5 carrying gears 29 rotatable on axes 33 and meshing with the internal annular gear I1 provided on a recessed support 3i located within the casing I5 is equipped with tubular hubs I8 and N and with an external annular gear I6 The casing I5 rotates freely in bearings 22 and 23* which are suitably mounted on the base 25 A high speed drive or input shaft i23 is journaled in bearings I21 which also are supported on the base 25 in any convenient manner. On one end of the drive or input shaft I23 a pinion Itii is rigidly mounted and meshes with the external annular gear Ni said drive shaft I23 also constituting part of a friction disc drive consisting of movable friction wheel I18, which is slidably mounted on said high speed or drive shaft I23 for instance, by means of a keyway I1I or the like. The friction wheel I19 is adjustable to any position on a friction disc I12 between stop rings I13 and I14 which are rigidly fastened on the drive shaft I23.

The friction disc I12 which rotates at right angles to the friction wheel I10 is fixed on a shaft I15 rotatable in a stationary bearing I16 suitably mounted on the base On the extreme end of the shaft I15 is rigidly mounted a bevel gear I11 which meshes with a bevel gear I18 mounted on the speed regulating shaft 26 The latter extends through and is rotatable in the tubular hub 2i of the casing I5 and carries on its inner end the pinion 28 which meshes with the gears 29. The output, or in this case slow speed shaft 32 forms part of the recessed support 3i carrying the internal annular gear I1 which meshes with the gears 29. The shaft 32 projects through and is rotatable in the tubular hub I8 and carries on its outer end a keyway 35 or its equivalent.

In operation, in order to effect zero speed or complete stop of the output shaft 32 the gear ratio and respective friction disc and friction wheel ratio must be such that gears 29 revolve inside of internal annular gear I1 This is accomplished by revolving pinion 28* at such a speed that the gears 29 do not develop any tooth pressure on the internal annular gear H The friction wheel I10 is set close to the center of the friction disc I12 thereby imparting to the latter the required high speed. In other words, the high speed or power input shaft I23 on which the friction wheel I10 is so mounted that it revolves With the shaft but may be axially shifted on this shaft I23 between the stop rings I13 and IE4, imparts rotative motion of the correct speed by means of the friction wheel I10 and the friction disc I12 and through shaft I15 and bevel gears I11 and I18 to the speed regulating shaft 26 and pinion 28 The high speed or power input shaft I23 also carries pinion I which meshes with and revolves the external annular gear ring IfS' of the hollow casing I5 This casing I5 carries the rotatable gears 29 which revolve at correlative speed with center pinion 28 so that the internal gear I1 and the output shaft 32 remain stationary. By shifting the friction wheel I10 alongthe high speed or input shaft I 23' towards the stop ring I14, the

contact diameter on the surface of the friction disc H2 is increased and the rotative speed of the latter decreased. As this is done and as the pinion 28 is directly connected with the friction disc I12 by means of the shaft I15, the bevel gears Ill and I73, and the speed regulating shaft 26, the speed ratio between the hollow casing I5 carrying the gears 28 and the internal annular gear I'I and the pinion 28 is changed.

The internal annular gear I'I and the thereto connected output shaft 32 compensate for this difference in ratio and start to revolve. The closer the friction wheel I70 is brought to the stop H4, the larger the contact diameter and the slower the friction disc I12 will revolve, which in turn will cause the output shaft 32 to rotate faster. When however the friction wheel H is brought near the center of the friction disc I12, a point will be reached where the output shaft 32' will stop rotating and where it will be in absolute non-rotatable or locked position.

In Fig. 13 is shown a differential gear arrangement connected to an infinitely variable speed control. In this combination the input shaft I23 of the variable speed control is connected at its outside end to a suitable prime mover, while at the other end it carries a pinion I3li; the latter meshes with an external annular gear I6 forming an integral part of the gear casing I which further is equipped with tubular central hubs I8 and 2 I, arranged to revolve in bearings 22 and 23 suitably supported on the base 25. In the casing I5 are internally mounted the shafts or axes I19 on which revolve the bevel gears I810. The speed regulating shaft 26 which rotates in and passes through the tubular hub 2 I on the gear casing I5, carries on its eX- ternally projecting portion a gear Zi and on its inner end within the casing I5 is provided with a bevel gear 28 meshing with the bevel'pinions I80. The output shaft 32 passes through and is rotatable in the tubular hub I8 of the gear casing I5and carries on its inner end within the latter the bevel gear I6! which also meshes with the bevel pinions I80. The shaft IBI of the variable speed reducing device, which normally is considered as the output shaft carries the gear I82 in mesh with the gear 21 of the speed regulating shaft 26.

The speed change unit illustrated in Fig. 13, consists of a box or frame I83 which rotatably supports the shafts I23 and I8I on each of which are mounted a pair of opposite conical wheels I84 and I35 between which a wedge shaped belt or chain IE3 transmits power. The efiective diameters of each pair of wheels can be altered under load to change the speed ratio, without steps. On changing the speed, the chain or belt I86 rises between wheels I85 and descends between the wheels I8 3, so that while the input shaft I23 connected to a suitable prime mover rotates at 28 rotate at such a speed that bevel gear "51 and output shaft 32 remain stationary.

When the speed ratio of the variable speed change unit is changed by altering the diameter of contact of the belt or chain I86 between the conical wheels I84 and I85, the output shaft I8I of the variable speed change unit revolves at a lower speed, thereby retarding the speed of gears 7 It is therefore evident that with the positive variable speed transmission gear the speed regulation is limited between predetermined high and low limits and in which case no zero speed or total stop can be obtained while the prime moveris in operation. 1 1

However, by coupling any of the herein described gear arrangements to the above described variable speed transmission gear, it is possible to bring about zero speed and a locked output shaft. 7

It is understood that any of the herein mentioned gear devicesmay be used in connection with any of the regulating devices described.

Basically the apparatus in all of its forms consists of an input shaft, an output shaft and a speed regulating shaft, any of the three shafts may take the place of any of the other two, depending upon whether an increase or decrease over the prime movers speed is required.

The three shafts are rotatively connected by means of gears in such a way tha the rotative speed of any two shafts influences the speed of the third shaft. 7

Thespeed variation; may be obtained by means of two hydraulic controls consisting'either of .a revolving cylinder variable displacement pump connected to a speed governor as in Figs. 1 and 2, or a combination of revolving cylinder variable speed constant displacement and variable displacement constant speed pump as in Figs. 8 and 9. The desired results according to the invention may also be obtained by means of a motor gene eratcr set consisting of two separately coupled units as in Fig. 11, a friction disc transmission as in Fig. 12, or by combination with a positive constant speed, the output shaft I8I changes its speed in accordance with the adjustment of the' belt or chain I355 on the wheels I85 and I85. It will be understood that suitable means is provided for efiecting the aforesaid adjustment of said belt or chain I85. By means of the gear I82 mounted to the output shaft I8I of the variable speed change unit, and gear 21 mounted to the speed regulating shaft 28, a ratio is established whereby if belt or chain I86 travels on the smallest diameters between the conical wheels I85 and the largest diameters between the conical wheels ass, the casing I5 and the internal gear infinitely variable speed regulating device as in Fig. 13. V v

Any suitable type of prime mover such as an electric motor, a steam turbine, an internal combustion engine, a wind mill, a wind rotor, a water wheel, or a Pelton wheel may be used in combination with the novel apparatus.

If the input shaft thereof is connected to a prime mover such as an electric motor, a steam turbine or a'steam engine, which operates at constant speed, the output shaft may be operatedand held at any speed between zero and the maximum output speed of the apparatus.

If the input shaft :of this apparatus is connected-to a prime mover such as'a wind mill or a wind rotor, whose speed varies, the output shaft may be maintained at constant speed or may be varied between zero and the maximum output speed possible.-

The prime mover such as an electric motor or steam turbine, directly connectedto the input shaft of the apparatus may be brought up to full operating speed, while the output shaft of the apparatus is at rest or zero speed, and said shaft may be brought up to any speed and be held at any rotative speed up to full output speed of the output shaft.

While the input shaft is rotating or is stopped, the output shaft, if not rotating, is held in a locked, stationary position so that it can not be rotated, and acts therefore as a positive brake to the output shaft and to the thereto connected working machine or rotative device.

Various changes in the specific forms shown and described may be made within the scope of the claims without departing from the spirit of the invention.

I claim:

1. In a variable speed apparatus, the combination of a planetary drive, an output shaft operatively controlled by said planetary drive, a speed regulating shaft operatively connected with said planetary drive, a speed variable displacement pump operatively connected with said speed regulating shaft, an oil circuit connected with said pump, an auxiliary pump connected with a source of oil supply and with said oil circuit for supplying oil thereto, said auxiliary pump being operatively connected with said planetary drive, an input shaft adapted for operative connection with a prime mover, and operatively connected with said planetary drive, gearing including a clutch pinion loosely mounted on said input shaft whereby the latter may be operatively connected with said speed variable displacement pump, a clutch whereby said clutch pinion is operatively connected with and disconnected from said input shaft, a control shaft, a cam gear loosely mounted on said last-named shaft and including worm gear teeth on a portion of its periphery and a depressed cam at another portion thereof, a bell crank lever, a roller carried by said bell crank lever in rolling engagement with the periphery of said cam gear in co-operative relation to said depressed cam, means controlled by said bell crank lever for operating said clutch to connect and disconnect the clutch pinion with and from said input shaft, a cam fixed on said control shaft, a lug projecting from the face of said cam gear in the path of said cam for operating said cam gear, a regulating shaft having a worm screw arranged to mesh with the worm gear teeth of said cam gear, an operating hand wheel fixed on said worm shaft, a pivotally mounted bearing bracket for said regulating shaft, means including an oil pressure controlled diaphragm for pivotally adjusting said bearing bracket to shift the worm screw into and out of mesh with the worm gear teeth of said cam gear, a stroke adjusting slide operatively connected with said control shaft for adjusting the displacement of said variable displacement pump to thereby control the operation of said planetary drive and the output shaft, a governor operatively connected with said output shaft, a governor valve in said oil circuit controlled by said governor and operated thereby in dependence upon the speed of said output shaft to develop and control resistance to the action of the variable displacement pump whereby the operation of the output shaft is controlled independently of variations in the speed of the input shaft, a three-way stopcock in the oil circuit for selectively directing the oil therein to said governor valve or through the circuit, and a twoway stop cock for controlling the flow through the circuit.

2. In a variable speed apparatus, the combination of a planetary drive, an output shaft operatively controlled by said planetary drive, a speed regulating shaft operatively connected with said planetary drive, a speedvariable displacement pump operatively connected with said speed regulating shaft, an oil circuit connected with said pump, an auxiliary pump connected with a source of oil supply and with said oil cir cuit for supplying oil thereto, said auxiliary pump being operatively connected with said planetary drive, an input shaft adapted for operative connection with a prime mover, and operatively connected with said planetary drive, gearing including a clutch pinion loosely mounted on said input shaft whereby the latter may be operatively connected with said speed variable displacement pump, a clutch whereby said clutch pinion is operatively connected with and disconnected from said input shaft, a control shaft, a cam gear loosely mounted on said last-named shaft and including worm gear teeth on a portion of its periphery and a depressed cam at another portion thereof, a bell crank lever, a roller carried by said bell crank lever in rolling engagement with the periphery of said cam gear in co-operative relation to said depressed cam, means controlled by said bell crank lever for operating said clutch to connect and disconnect the clutch pinion with and from said input shaft, a cam fixed on said control shaft, a lug projecting from the face of said cam gear in the path of said cam for operating said cam gear, a regulating shaft having a worm screw arranged to mesh with the worm gear teeth of said cam gear, an operating hand wheel fixed on said worm shaft, a pivotally mounted bearing bracket for said regulating shaft, means including an oil pressure controlled diaphragm for pivotally adjusting said bearing bracket to shift the worm screw into and out of mesh with the worm gear teeth of said cam gear, a stroke adjusting slide operatively connected with said control shaft for adjusting the displacement of said variable displacement pump to thereby control the operation of said planetary drive and the output shaft, a governor operatively connected with said output shaft, and a governor valve in said circuit controlled by said governor and operated thereby in dependence upon the speed of said output shaft to develop and control resistance to the action of do said variable displacement pump whereby the output shaft is controlled independently of variations in the speed of the input shaft.

3. In a variable speed apparatus, the combination of a planetary drive, an output shaft operatively controlled by said planetary drive, a speed regulating shaft operatively connected with said planetary drive, a speed variable displacement mover, and operatively connected periphery and a depressed cam at another portion thereof, a bell crank lever, a roller carried by said bell crank lever in rolling engagement with the periphery of said cam gear in co-operative relation to said depressed cam, means controlled by said bell crank lever for operating said cinch to connect and disconnect the clutch pinion with and from said input shaft, a cam fixed on said control shaft, a lug projecting from the face of said cam gear in the path of said cam for operating said cam gear, a regulating shaft having a worm screw arranged to mesh with the worm gear teeth of said cam gear, an operating hand wheel fixed on said worm shaft, a pivotally mounted bearing bracket for said regulating shaft, means including an oil pressure controlled diaphragm for pivotally adjusting said bearing bracket to shift the worm screw into and out of mesh with the worm gear teeth of said cam gear, a stroke adjusting slide operatively connected with said control shaft for adjusting the displacement of said variable displacement pump to thereby control the operation of said planetary drive and the output shaft, and a governor controlled valve in said circuit operated in dependonce upon the speed of said output shaft to control the latter independently of variations in the speed of the input shaft.

ERNEST GROSSENBl'iCI-IER. 

